CN104564873A - Single-load hydraulic system and machine - Google Patents
Single-load hydraulic system and machine Download PDFInfo
- Publication number
- CN104564873A CN104564873A CN201310506844.9A CN201310506844A CN104564873A CN 104564873 A CN104564873 A CN 104564873A CN 201310506844 A CN201310506844 A CN 201310506844A CN 104564873 A CN104564873 A CN 104564873A
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- Prior art keywords
- hydraulic system
- hydraulic
- variable displacement
- fluid
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- 239000012530 fluid Substances 0.000 claims abstract description 72
- 238000006073 displacement reaction Methods 0.000 claims description 57
- 238000005086 pumping Methods 0.000 claims description 8
- 239000002828 fuel tank Substances 0.000 description 7
- 238000004134 energy conservation Methods 0.000 description 3
- 239000000284 extract Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 244000287680 Garcinia dulcis Species 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Power Steering Mechanism (AREA)
Abstract
The invention relates to a hydraulic system (10) used for a machine. The hydraulic system comprises a hydraulic steering system (11), a working hydraulic system (12), a variable pump (14) and a metering pump (16), wherein the variable pump (14) is used for supplying hydraulic fluid for the hydraulic steering system, and the metering pump (16) is used for supplying the hydraulic fluid for the working hydraulic system; the variable pump is selectively in fluid communication with the hydraulic steering system and the working hydraulic system through a priority valve. The hydraulic system is characterized in that the priority valve is provided with an LS port (133); the LS port is used for receiving a load feedback pressure signal (LS) from the hydraulic steering system when the hydraulic steering system works, and moreover, the priority valve is structured to supply the hydraulic fluid pumped by the variable pump to the hydraulic steering system preferentially when the hydraulic steering system works.
Description
Technical field
Present invention relates in general to a kind of hydraulic system, relate more specifically to a kind of single load-sensitive hydraulic system and comprise the machine of this hydraulic system.
Background technique
The such as machine of wheel loader, excavator, bulldozer, grader or other type jumbo and so on uses the multiple actuators be supplied from the hydraulic fluid of the one or more pumps on machine to complete various task usually.Existing hydraulic system mainly comprises two metering pump autonomous system, two metering pump converging system, bivariate pump autonomous systems etc.The shortcoming that these hydraulic systems exist is, all there is not energy-conservation defect in two metering pump autonomous system and converging system, particularly when machine is idle, necessarily or when change system energy loss is under back pressure had in the engine speed of machine, bivariate pumping system then cost higher and control more complicated, and require very high to the turbidity test of oil product under severe operating mode, this makes how to ensure that the turbidity test of oil product become a problem.
In addition, in prior art, also single load-sensitive hydraulic system of core valve is opened in known use, uses a variable displacement pump for steering hydraulic system and a metering pump for hydraulic system of working in such systems.This hydraulic system adopts and turns to preferential hydraulic control method, when machine turns to, variable displacement pump is preferentially to steering hydraulic system fuel feeding, and when machine does not turn to, the hydraulic fluid that can export with metering pump at least partially of the hydraulic fluid exported by variable displacement pump collaborates and is supplied to hydraulic system of working, and working tool is more effectively worked.But a shortcoming of this hydraulic system can not keep flow minimum in hydraulic system under machine holding state.
The present invention is intended to overcome above-mentioned one or more problem and/or the other problem of prior art.
Summary of the invention
In an aspect, the present invention relates to a kind of hydraulic system for machine, this hydraulic system comprises steering hydraulic system, hydraulic system of working, for the variable displacement pump to steering hydraulic system supplying hydraulic fluid, with for the metering pump to hydraulic system of working supplying hydraulic fluid, wherein, described variable displacement pump is optionally communicated with hydraulic system of working fluid with steering hydraulic system by pressure-gradient control valve, it is characterized in that, described pressure-gradient control valve has a LS mouth, this LS mouth is used for the load feedback pressure signal received when steering hydraulic system works from steering hydraulic system, and described pressure-gradient control valve is configured to preferentially be supplied to steering hydraulic system when steering hydraulic system works by the hydraulic fluid of variable displacement pump pumping.
Advantageously, described pressure-gradient control valve is connected to sequence valve by one-way valve fluid, described sequence valve fluid is connected to hydraulic system of working, and described hydraulic system comprises the control valve of the output flow for controlling described variable displacement pump, when machine is in holding state, described sequence valve cuts out, and makes to flow to described control valve so that the output flow of variable displacement pump is adjusted to smaller value by the hydraulic fluid of variable displacement pump pumping, thus reaches energy-conservation object.
In one aspect of the method, the present invention relates to a kind of machine comprising described hydraulic system.
Accompanying drawing explanation
In more detail the present invention is described below with reference to schematic accompanying drawing.Accompanying drawing and corresponding embodiment are only for illustrative purposes, but not for limiting the present invention.In the accompanying drawings:
Fig. 1 schematically shows according to hydraulic system of the present invention,
Fig. 2 illustrates the pressure-gradient control valve used in the hydraulic system of Fig. 1, and
Fig. 3 is the partial schematic diagram according to hydraulic system of the present invention.
Embodiment
Fig. 1 schematically shows according to the hydraulic system 10 for a machine, such as wheel loader of the present invention, and simultaneously see Fig. 3, hydraulic system 10 comprises steering hydraulic system 11 and hydraulic system of working 12.Steering hydraulic system 11 comprises variable displacement pump 14, and this variable displacement pump 14 is for extracting hydraulic fluid from fuel tank 21 and the steering gear (such as wheel) 22 hydraulic fluid being delivered to machine turns to make machine.Hydraulic system of working 12 comprises metering pump 16, this metering pump 16 for extract hydraulic fluid from fuel tank 21 and the working tool 26 hydraulic fluid being delivered to machine to realize different tasks.Working tool can be embodied as scraper bowl, fork arrangement, advancing means, cutting device, scoop, snow breaker or other task execution device any known in the art.Working tool can complete various action under the driving of hydraulic fluid, such as lifting, inclination, pivotable, rotation, swing or other motion known in the art.
As shown in Figure 1, metering pump 16 is connected with working tool 26 fluid via driving core valve 24, makes working tool can be driven by metering pump 16 to realize the action expected from the hydraulic fluid that fuel tank 21 extracts.In addition, hydraulic fluid can return fuel tank 21 from working tool 26 through driving core valve 24.
The output terminal of variable displacement pump 14 is connected with pressure-gradient control valve 13 fluid.Fig. 2 shows in detail the schematic diagram of pressure-gradient control valve 13.Pressure-gradient control valve 13 has input port 130 and two output ports 131,132, wherein, the output terminal of variable displacement pump 14 is connected with input port 130 fluid of pressure-gradient control valve 13, output port 131 is connected with the input port fluid of sequence valve 18 via an one-way valve 17, and sequence valve 18 is connected with working tool 26 fluid via driving core valve 24.Another output port 132 of pressure-gradient control valve 13 is connected with the steering gear 22 fluid of machine.When the input port 130 of pressure-gradient control valve 13 is communicated with output port 132 fluid, the steering gear 22 of machine can be flow to through pressure-gradient control valve 13 from the hydraulic fluid that fuel tank 21 extracts by variable displacement pump 14, thus realize the steering operation of expectation.In addition, hydraulic fluid can return fuel tank 21 from the steering gear 22.
Except input port 130 and two output ports 131,132, pressure-gradient control valve 13 also comprises the LS mouth 133 be connected with the control port fluid of the steering gear 22, and the load feedback pressure LS from the steering gear 22 can arrive LS mouth 133 via control channel 28.Pressure-gradient control valve 13 comprises spool and the spring 5 to right side this spool of bias voltage in Fig. 2 in addition.When the hydraulic fluid from variable displacement pump 14 arrives input port 130, hydraulic fluid is preferentially supplied to output port 132 through spool.When the steering gear 22 does not work, output port 132 is in closed state, now, the pressure of LS mouth is zero, hydraulic fluid acts on the right-hand member of spool, overcome spring 5 and act on biasing force on spool, spool is moved towards the left side in Fig. 2, and the input port 130 of pressure-gradient control valve 13 is communicated with output port 131 fluid.Like this, hydraulic fluid from variable displacement pump 14 flows to one-way valve 17 through pressure-gradient control valve 13, and sequence valve 18 is connected, thus make the hydraulic fluid from variable displacement pump 14 be transported to hydraulic system of working 12 together with the hydraulic fluid from metering pump 16, two pumps 14 and 16 operate under the state of interflow, and the efficiency of hydraulic system 10 is increased.
As shown in figs. 1 and 3, hydraulic system 10 according to the present invention also comprises shuttle valve 15.As known in the art, shuttle valve 15 comprises two input ports and an output port.The first input end mouth 151 of shuttle valve 15 is connected to receive the load feedback pressure signal LS of the steering gear 22 from steering hydraulic system with steering hydraulic system 11 fluid, and the second input port 152 is connected to receive the pressure signal from hydraulic system of working with hydraulic system of working 12 fluid.The output port 153 of shuttle valve 15 is connected with control valve 19 fluid for variable displacement pump 14, to send the pressure signal received to variable displacement pump 14, promote the swash plate of variable displacement pump 14, thus controlled variable pump 14 works.If only steering hydraulic system 11 works, then shuttle valve 15 the load feedback pressure signal LS of in the future low damage device 22 can be sent to variable displacement pump 14.If only hydraulic system of working 12 works, then the pressure signal from hydraulic system of working can be sent to variable displacement pump 14 by shuttle valve 15.If steering hydraulic system 11 and hydraulic system of working 12 are all in work, then two input ports of shuttle valve 15 act on the pressure signal had from steering hydraulic system 11 and hydraulic system of working 12 simultaneously respectively, now send wherein larger pressure signal to variable displacement pump 14.Especially as seen from Figure 3, the output terminal of variable displacement pump 14 also fluid is connected to control valve 19, when the pressure that variable displacement pump 14 exports is enough large with the balanced type breaking control valve 19, the pressure difference value Δ p(margine pressure overcoming control valve 19) time, control valve 19 conducting can lead to the stream of the control oil cylinder 20 of variable displacement pump 14, promote the swash plate oil cylinder of variable displacement pump 14 thus, change swash plate pivot angle, thus the output flow of Moderator Variable pump 14.
When machine carries out steering operation, output port 132 is communicated with the steering gear 22 fluid, and the hydraulic fluid from variable displacement pump 14 arrives the steering gear 22, and machine is turned to.From the steering gear 22 load feedback pressure LS by after throttle valve through to be acted on the left end of spool by the LS mouth 133 of pressure-gradient control valve 13.When the rotating speed of the steering gear is very large, thus when load feedback pressure LS is enough large, the spool of pressure-gradient control valve 13 can be made to move towards the right side in Fig. 2.Now, the input port 130 of pressure-gradient control valve 13 is communicated with output port 132 fluid.Hydraulic fluid from variable displacement pump 14 flows to steering hydraulic system 11, thus realizes the go to action of expectation.
Should be appreciated that pressure-gradient control valve 13 can be Proportional valve type, its spool can move pro rata according to the pressure difference acted between spool two ends.Therefore, along with the change of the load feedback pressure LS from the steering gear 22, the hydraulic fluid extracted by variable displacement pump 14 can distribute between the output port 131 and 132 of pressure-gradient control valve 13.Like this, as required, the part from the hydraulic fluid of variable displacement pump 14 can be supplied to steering hydraulic system 11, and another part then can be supplied to hydraulic system of working 12 together with the hydraulic fluid from metering pump 16.
Advantageously, pressure-gradient control valve 13, one-way valve 17, sequence valve 18 and shuttle valve 15 can be designed to Cartridge inserted valve integrated block, save the arrangement space of hydraulic system 10 thus.
Below the various working staties of hydraulic system 10 are described in detail.
Industrial usability
When the steering hydraulic system 11 of machine does not work, and hydraulic system of working 12 is when working, the load feedback pressure signal acting on the first input end mouth 151 of shuttle valve 15 is zero, and the pressure signal from hydraulic system of working 12 is sent to variable displacement pump 14 by shuttle valve 15, starts variable displacement pump 14 and works.Now, the load feedback pressure LS at LS mouth 133 place of pressure-gradient control valve 13 is also zero, the pressure acting on the hydraulic fluid of the spool right-hand member of pressure-gradient control valve 13 overcomes spring 5 and acts on spring force on spool, and this spool is moved to the left side in Fig. 2, and input port 130 is communicated with output port 131 fluid.Hydraulic fluid from variable displacement pump 14 collaborates with the hydraulic fluid from metering pump 16 via one-way valve 17 and sequence valve 18, then be transported to working tool 26 via driving core valve 24 together, metering pump 16 and variable displacement pump 14 provide hydraulic fluid to hydraulic system of working jointly thus.
When the steering hydraulic system 11 of machine works, and hydraulic system of working 12 is not when working, the pressure signal acting on the second input port 152 of shuttle valve 15 is zero, and the load feedback pressure signal LS of shuttle valve 15 low damage hydraulic system in future 11 is sent to variable displacement pump 14, starts variable displacement pump 14 and works.Simultaneously, the spool of pressure-gradient control valve 13 is jointly made to move to the right side in Fig. 2 from the load feedback pressure LS of the steering gear 22 and the spring 5 of pressure-gradient control valve 13, the input port 130 of pressure-gradient control valve 13 is communicated with output port 132 fluid thus, hydraulic fluid from variable displacement pump 14 flows to steering hydraulic system 11, thus realizes the go to action of expectation.
When the steering hydraulic system 11 of machine and hydraulic system of working 12 all work, load feedback pressure signal LS from steering hydraulic system 11 acts on the first input end mouth 151 of shuttle valve 15, and the pressure signal from hydraulic system of working 12 acts on the second input port 152 of shuttle valve 15.Now, larger one in these two pressure signals is sent to variable displacement pump 14 by shuttle valve 15, starts variable displacement pump 14 and works.Simultaneously, the spool of pressure-gradient control valve 13 moves under the load feedback pressure signal LS from steering hydraulic system 11 and the acting in conjunction from the hydraulic fluid of variable displacement pump 14, make a part from the hydraulic fluid of variable displacement pump 14 by priority of supply to steering hydraulic system 11, realize the go to action expected, remaining part is supplied to hydraulic system of working 12 after then collaborating with the hydraulic fluid from metering pump 16.
When machine is in holding state, steering hydraulic system 11 and hydraulic system of working 12 do not work.Now, the steering gear does not produce any load feedback pressure signal LS, and the input port 130 of pressure-gradient control valve 13 is communicated with output port 131 fluid.From the hydraulic fluid of variable displacement pump 14 through pressure-gradient control valve 13 and one-way valve 17 order of arrival valve 18 place.Hydraulic fluid in hydraulic system of working 12 directly returns fuel tank 21, and cause the circuit pressure of hydraulic system of working 12 lower, sequence valve 18 cuts out, and is now flowed to the control valve 19 of variable displacement pump 14 by the hydraulic fluid of variable displacement pump 14 pumping.The pressure exported by variable displacement pump 14 rises gradually, until break the balanced type of control valve 19, overcome the pressure difference value Δ p(margine pressure of control valve 19), control valve 19 conducting is made to lead to the stream (see accompanying drawing 3) of the control oil cylinder 20 of variable displacement pump 14, promote the swash plate oil cylinder of variable displacement pump 14, the swash plate pivot angle controlling oil cylinder 20 controlled variable pump 14 is very little to the output flow of variable displacement pump 14, thus realizes energy-conservation object.
By specific embodiment, hydraulic system of the present invention is described above.It will be readily apparent to one skilled in the art that and can make multiple change and distortion to hydraulic system of the present invention without departing from the present invention in the case of the inventive idea.In conjunction with to the consideration of specification and the practice of disclosed hydraulic system, other embodiment will be apparent to those skilled in the art.Specification and example are only regarded as exemplary, and real scope is represented by following claim and their equivalent.
Claims (6)
1. the hydraulic system for machine (10), comprise steering hydraulic system (11), hydraulic system of working (12), for the variable displacement pump (14) to steering hydraulic system supplying hydraulic fluid, with for the metering pump (16) to hydraulic system of working supplying hydraulic fluid, wherein, described variable displacement pump is optionally communicated with hydraulic system of working fluid with steering hydraulic system by pressure-gradient control valve (13), it is characterized in that, described pressure-gradient control valve has a LS mouth (133), this LS mouth is used for the load feedback pressure signal (LS) received when steering hydraulic system works from steering hydraulic system, and described pressure-gradient control valve is configured to preferentially be supplied to steering hydraulic system when steering hydraulic system works by the hydraulic fluid of variable displacement pump pumping.
2. hydraulic system according to claim 1, wherein, described pressure-gradient control valve is connected to sequence valve (18) by one-way valve (17) fluid, described sequence valve fluid is connected to hydraulic system of working, and described hydraulic system comprises the control valve (19) of the output flow for controlling described variable displacement pump, when machine is in holding state, described sequence valve cuts out, and makes to flow to described control valve (19) so that the output flow of variable displacement pump is adjusted to smaller value by the hydraulic fluid of variable displacement pump pumping.
3. hydraulic system according to claim 1 and 2, wherein, described hydraulic system comprises shuttle valve (15), described shuttle valve is used for the described load feedback pressure signal of low damage hydraulic system in the future and is sent to variable displacement pump from one higher in the pressure signal of hydraulic system of working, with controlled variable pump work.
4. according to hydraulic system in any one of the preceding claims wherein, wherein, described pressure-gradient control valve is configured to make collaborating with the hydraulic fluid by metering pump pumping at least partially and being supplied to hydraulic system of working by the hydraulic fluid of variable displacement pump pumping when described hydraulic system of working work.
5. according to hydraulic system in any one of the preceding claims wherein, wherein, described pressure-gradient control valve, one-way valve, sequence valve and shuttle valve are configured to a Cartridge inserted valve integrated block.
6. a machine, comprises according to hydraulic system in any one of the preceding claims wherein.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310506844.9A CN104564873B (en) | 2013-10-24 | 2013-10-24 | Single load hydraulic system and machine |
| RU2014142887A RU2678475C2 (en) | 2013-10-24 | 2014-10-23 | Single-load hydraulic system and machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310506844.9A CN104564873B (en) | 2013-10-24 | 2013-10-24 | Single load hydraulic system and machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104564873A true CN104564873A (en) | 2015-04-29 |
| CN104564873B CN104564873B (en) | 2018-12-21 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310506844.9A Active CN104564873B (en) | 2013-10-24 | 2013-10-24 | Single load hydraulic system and machine |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN104564873B (en) |
| RU (1) | RU2678475C2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110345136A (en) * | 2018-04-06 | 2019-10-18 | 雷蒙德股份有限公司 | Auxiliary circuit filtration system and method |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU191188U1 (en) * | 2019-05-07 | 2019-07-29 | Маргарита Викторовна Минеева | TRACTOR HYDRAULIC SYSTEM |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5579642A (en) * | 1995-05-26 | 1996-12-03 | Husco International, Inc. | Pressure compensating hydraulic control system |
| GB2324575A (en) * | 1997-04-24 | 1998-10-28 | Caterpillar Inc | Load sense hydraulic system |
| CN2610133Y (en) * | 2003-03-14 | 2004-04-07 | 柯坚 | Quantitative variable confluent system of loader |
| CN201169289Y (en) * | 2008-01-29 | 2008-12-24 | 广西柳工机械股份有限公司 | Forklift load sensing priority steering hydraulic system |
| CN101954927A (en) * | 2010-10-19 | 2011-01-26 | 中国人民解放军总装备部军械技术研究所 | Multi-load hydraulic sensing system for single-power source and multi-system working |
| CN203113417U (en) * | 2012-12-28 | 2013-08-07 | 龙工(上海)机械制造有限公司 | Univariate hydraulic system of loading machine |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2160696C2 (en) * | 1997-10-31 | 2000-12-20 | Стесин Александр Борисович | Fork-lift truck hydraulic system |
| RU13205U1 (en) * | 1999-12-06 | 2000-03-27 | Открытое акционерное общество Тверской экскаваторный завод | FORKLIFT HYDRAULIC SYSTEM |
| RU84878U1 (en) * | 2009-04-22 | 2009-07-20 | Общество с ограниченной ответственностью "Инженерный центр" | HYDRAULIC DRIVER OF A SINGLE LOAD LOADER |
-
2013
- 2013-10-24 CN CN201310506844.9A patent/CN104564873B/en active Active
-
2014
- 2014-10-23 RU RU2014142887A patent/RU2678475C2/en active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5579642A (en) * | 1995-05-26 | 1996-12-03 | Husco International, Inc. | Pressure compensating hydraulic control system |
| GB2324575A (en) * | 1997-04-24 | 1998-10-28 | Caterpillar Inc | Load sense hydraulic system |
| CN2610133Y (en) * | 2003-03-14 | 2004-04-07 | 柯坚 | Quantitative variable confluent system of loader |
| CN201169289Y (en) * | 2008-01-29 | 2008-12-24 | 广西柳工机械股份有限公司 | Forklift load sensing priority steering hydraulic system |
| CN101954927A (en) * | 2010-10-19 | 2011-01-26 | 中国人民解放军总装备部军械技术研究所 | Multi-load hydraulic sensing system for single-power source and multi-system working |
| CN203113417U (en) * | 2012-12-28 | 2013-08-07 | 龙工(上海)机械制造有限公司 | Univariate hydraulic system of loading machine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110345136A (en) * | 2018-04-06 | 2019-10-18 | 雷蒙德股份有限公司 | Auxiliary circuit filtration system and method |
Also Published As
| Publication number | Publication date |
|---|---|
| RU2014142887A (en) | 2016-05-20 |
| RU2678475C2 (en) | 2019-01-29 |
| CN104564873B (en) | 2018-12-21 |
| RU2014142887A3 (en) | 2018-07-30 |
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